Drive mechanism



May 27, 1969 c, w, o w ET AL 3,446,087

DRIVE MECHANISM Filed July 28, 1967 Sheet of 2 48 I4 92 INVENTOR.

'- CHARLES W. BROUWER RAYMOND V. TATA F|G.6 wai M,

ATTOR'NEYS M y 1969 c. w. BROUWER ET AL 3,446,087

7 DRIVE MECHANISM Filed July 28, 1967 Sheet 2 of2 INVENTOR. CHARLES W. BROUWER BY RAYMON v. 44 48 f a -q. M14 as United States Patent US. Cl. 74-190 19 Claims ABSTRACT OF THE DISCLOSURE A winding machine having a drive mechanism supporting a drive roll on a drive shaft. The mechanism is selectively operable to drive the drive roll in forward and reverse directions and to brake the drive roll.

The invention relates generally to improvements in drive mechanisms employing bearings of the rolling element variety.

Throughout the following specification and claims, the term yarn is employed in a general sense to apply to all kinds of strand material, either textile or otherwise, and the term package means the product of a winding or twisting machine, whatever its form.

It is customary in textile winding operations to employ a rotatable drive roll in surface-to-surface engagement with a take-up package for driving the package and guiding a strand of yarn .onto the package. In the course of winding, the yarn may be interrupted as when a break occurs in the yarn or when a supply bobbin is exhausted. It is then necessary to join the free end from the supply bobbin to the free end from the take-up package in order to resume winding and, as part of this procedure, the take-up package is rotated in a direction opposite that of normal winding in order to unwind a length of the free end of the yarn.

Previous arrangements for driving the take-up package often employ elaborate clutch mechanisms which are generally unsatisfactory, complicated, and costly. In other previous arrangements, relatively complex mechanisms are employed to remove the take-up package from surface engagement with the drive roll, then brake the package to a halt, and thereupon move it to a reversing position in which it engages an oppositely rotating drive roll.

Briefly, the invention is directed to a novel bearing and drive mechanism for the drive roll of a winding machine. In one embodiment the drive roll is rotatably supported on a drive shaft by a first rolling element bearing. Axially spaced from the first bearing is a second rolling element bearing on the drive shaft. Each of these bearings is radially pre-loaded and their rolling elements are provided with a common retainer. During normal winding operations, the drive mechanism connects the drive roll with the drive shaft for winding the yarn. However, the drive mechanism may be operated to disengage the drive roll from the drive shaft and brake the drive roll to a halt, and thereupon to reverse the drive roll. In another embodiment, the drive mechanism is operated to disengage the drive roll from the drive shaft, and the drive roll is then driven in reverse.

Accordingly, it is a primary object of the invention to provide an improved drive mechanism.

It is a further object of the invention to provide an improved multi-speed drive mechanism.

Another object of the invention is to provide a novel mechanism which serves simultaneously to support and to rotate a roll.

A further object of the invention is to provide a new and improved mechanism for selectively driving and braking a rotatable member.

Yet a further object of the invention is to provide a new and improved multi-speed drive mechanism employing bearings of the rolling element variety and including control means for selectively adjusting the output speed of the drive mechanism.

Still a further object of the invention is to provide a new and useful mechanism for simultaneously rotating and supporting a drive roll of a textile winding machine, the mechanism being coaxial with the drive roll and selectively operable to rotate the drive roll in forward and reverse directions. A related object is the provision of mechanism for braking the roll.

Yet another object of the invention is to provide a new and useful mechanism having an armature axially movable from one position connecting a driven member with a magnetic driving member to another position connecting the driven member with a relatively stationary part for braking the driven member.

Other and further objects and advantages of the invention will be apparent from the following description and the accompanying drawings, in which:

FIG. 1 is a fragmentary end elevation view schematically illustrating a portion of an automatic winding machine embodying the invention, with parts broken away for clearer illustration;

FIG. 2 is an enlarged, fragmentary side view with parts broken away generally along the line 2-2 in FIG. 1 and illustrating one operating position of certain parts;

FIG. 3 is a fragmentary section view of a portion of FIG. 2, illustrating a different operating position of the P FIG. 4 is a fragmentary sectional view, similar to that shown in FIGS. 2 and 3, but illustrating still a different operating position of the parts;

FIG. 5 is a fragmentary end elevation view similar to FIG. 1 schematically illustrating another embodiment of the invention, with parts broken away for clearer illustration; and

FIG. 6 is a fragmentary section view taken substantially along lines 66 of FIG. 5.

Refer to the drawings, and in particular to FIG. 1 which illustrates a portion of a winding machine 10 embodying the present invention. A generally cylindrical drive roll 12 is supported upon a drive mechanism including a drive shaft 14, and has helical grooves 16 (see FIG. 2) in its cylindrical surface. A take-up package P is rotatably mounted in position to be driven by surface engagement with the drive roll 12. As the package P and drive roll 12 rotate, a strand of yarn Y is guided to and fro across the surface of the package by means of the groove 16.

Suitable bearings support the drive roll on the shaft 14, and as seen in FIG. 2, a cylindrical axial recess 18 is formed at an end of the drive roll 12 for receiving a supporting or first bearing member 20 of a bearing-drive unit 21. The supporting bearing 20 includes an inner race 22 fixedly seated on the drive shaft 14 and an outer race 24 fixedly seated on the cylindrical surface of the axial recess 18 to rotatably support the drive roll 12 on the drive shaft 14. The races 22 and 24 are respectively grooved to receive therebetween a plurality of balls 26. Other bearings (not shown) may also support the roll 12 A driving assembly for the roll 12 includes a second bearing member 28, of the bearing-drive unit 21, within the axial recess 18 and axially spaced from the first hearing 20. The bearing 28 includes an inner race 30 fixedly seated on the drive shaft 14, an outer race 32 spaced from the inner cylindrical surface of the axial recess 18, and a plurality of balls 34 disposed between the races 30 and 32. The outer race 32 of the second bearing 28 3 extends past (to the left in FIG. 2) the inner race and a retainer 36. A single ball retainer 36 is common to the balls 26 and 34 of the respective bearings.

To the left of the second bearing 28 as seen in FIG. 2, is a non-magnetic or paramagnetic collar 38 releasably fixed to the shaft 14 as by a set screw 40; A ring-shaped permanent magnet 42 is suitably bonded to the lateral surface of the collar 38 facing the bearing 28. A central bore 44 in the magnet is of a diameter greater than the shaft 14 to provide an annular clearance between the shaft and the magnet. Disposed between the magnet '42 and the second bearing 28 is a coupling member in the form of a disc-shaped ferromagnetic armature 46. The armature 46 has a central aperture 48 so as to be freely received on the drive shaft 14 with the disc withina recess 50 formed at the end of the roll 12. Thus, the armature 46 has freedom of axial movement within the limits defined by the magnet 42 and the second bearing outer race 32.

A plurality of axially extending threaded bores 52 in an end face of the drive roll 12 threadedly receive screws 54 passing through holes 55 in an annular connecting element or member 56 at the end of the drive roll 12. The screws 54 extend freely through the holes 55 and receive helical compression springs 60 between the screw heads and the member 56, so that the latter is urged rightwardly (FIG. 2) against a lateral surface 62.

As seen in FIGS. 1 and 2, a stationary supporting bracket 64 of a frame of the winding machine 10 forms a base including a circular housing 66 having a radially outwardly directed flange 68. A plurality of fingers 70 are attached to the flange 68 at circumferentially spaced locations by screws 72 and extend axially toward the drive roll 12 with inwardly directed ends 73 about a ring 74 to hold the ring against the circular housing 66. A plurality of radially inwardly extending cam guide pins 76 are fixedly embedded in the rings 74 and are freely received in cam grooves 77 in a hollow cylinder 78 supported by the circular housing 66. The cylinder 78 is free to move axially relative to the ring 74 and the housing 66 and against the armature 46. It is held against rotation -by means of a key 80 seated in cooperating slots in the cylinder 78 and the circular housing 66. The grooves 77 are so formed that when the ring 74 is rotated in the counterclockwise direction, as seen in FIG. 1, the cylinder 78 and therefore the armature 46 is moved to the right, as seen in FIG. 2, and conversely. Rotation of the ring 74 is provided by an actuating rod 86 which extends downwardly from an car 87 on the ring 74 to a control link of a control unit 88 (see FIG. 1) of the winding machine 10.

During winding operations the package P is rotatably driven by the drive roll 12 and yarn Y is guided onto and across the outer surface of the package P by the helical grooves 16. As seen in FIG. 2, the drive roll- 12 is drivingly coupled to the drive shaft for rotation at shaft speed with the armature 46 drawn firmly against the magnet 42 and with the annular member 56 therefore compressing the springs 60. Thus, in FIG. 2, the drive roll 12 is connected to the drive shaft 14 via screws 54, member 56, armature 46, magnet 42, and finally collar 38. It should be noted that the screws 54 serve to adjust the compressive force in each of the springs 60, which, in turn, determine the bearing force between the armature 46 and the annular member 56. Since the acceleration of the drive roll 12 from a slower speed to operational speed varies in relation to the bearing force between the armature 46 and the annular member 56 (as well as the magnet 42), the screws 54 serve to regulate the rate of acceleration. Although it may be preferable, for the operation of the invention, to draw the armature 46 firmly against the magnet 42, this is not a necessary condition in that the armature 46 may be slightly spaced from the magnet and yet remain sufiiciently within the magnetic field thereof to rotate the drive roll 12.

To stop the drive roll, the control unit 88 causes the actuating rod 86 to rise thereby rotating the ring 74 in a counterclockwise direction (FIG. 1) and through the cooperating guide pins 76 and cam grooves 77 the nonrotatable cylinder 78 is moved to the right and its end surface bears against the armature 46 and urges the armature rightwardly away from the magnet 42 to an intermediate position (see FIG. 3). The armature 46 continues to engage the annular member 56 and is firmly held against the member by the force of the magnetic attraction between the magnet 42 and the armature 46. Thus, the drive roll 12 is operatively connected with the stationary bracket 64 via the screws 54, annular member 56, armature 46, and the non-rotating cylinder 78. The springs 60 are of sufficient strength to assure a firm engagement between the armature 46 and the annular member 56. Thus engaged with a non-rotating part, the drive roll 12 is slowed and brought to a stop.

To reverse the direction of rotation of the drive roll 12, the control unit 88 causes the actuating rod 86 to rise to a still higher position whereupon the cylinder 78 is moved farther to the right. When the armature 46 has reached its extereme (or second) position (FIG. 4), it is in engagement with the non-rotatable cylinder 78 and the outer race 32 of the second bearing 28, which, as previously discussed, extends leftwardly (FIG. 2) beyond the inner race 30 and retainer 36 of the bearing 28. The outer race 32 is thus held stationary. Since the inner race 30 rotates with the shaft 14, the balls 34 are caused to roll along the outer race 32 and carry the retainer 36 along with them. The retainer 36 in turn rotates the balls 26 along the inner race 22 and carry the outer race 24 with them so that the outer race 24 rotates the drive roll 12 in reverse. The bearings 20 and 28 cooperate in such a manner that when the outer race 32 of the bearing 28 is held stationary, the outer race 24 of the bearing 20 will rotate according to the following mathematical relationship for every revolution of the drive shaft 14:

. AY-BZ Revolutions of Y- wherein:

Y denotes the maximum diameter of the rolling surface of the outer race 24;

Z denotes the minimum diameter of the rolling surface of the inner race 22;

B denotes the maximum diameter of the rolling surface of the outer race 32; and

A denotes the minimum diameter of the rolling surface of the inner race 30.

Thus, when appropriate values have been chosen for A, B, Y, and Z the solution to the above mathematical relationship can be made a negative value. The signficance of a negative value of Revolutions of Y is that the outer race 24 and therefore the drive roll 12 rotates in a direction opposite that of drive shaft 14 and at a speed equal to the magnitude of the solution. For example, in the illustrated embodiment, the following bearing dimensions will give the desired results: Y=2.062 inches, Z==1.437 inches, B=2.187 inches, and A=l.437 inches.

Thus the take-up package P can be reverse rotated while remaining in surface engagement with the drive roll 12, and the reversal of the package P is achieved by a simple, inexpensive, and compact mechanism which serves not only to drive the drive roll 12 but also to support the drive roll on the drive shaft 14.

Even when the armature 46 is in the extreme or second position (FIG. 4), it remains within the field of the magnet 42. Thus, upon completion of the end finding operation, at which time the control unit 88 lowers the actuating rod 86, the armature is drawn leftwardly from the second position indicated in FIG. 4, to the intermediate position in FIG. 3 to brake the drive roll 12 and the package P, and then to the first position as indicated in FIG. 2 to again drive the package in the forward or winding direction.

Another embodiment of the invention is shown in FIGS. 5 and 6 wherein all reference numerals remain unchanged from the views illustrating the previous embodiments except when reference is made to modified elements thereof. The drive roll 12 is rotatably supported on the drive shaft 14 by means of a bearing 90 which need not be of the pre-loaded variety as in the previous embodiment. The bearing 90 includes an inner race 92 fixedly seated on the drive shaft 14 and an outer race 94 fixedly seated on the cylindrical surface of the axial recess 18. The races 92 and 94 are respectively grooved to receive therebetween a plurality of balls 96 which are held in spaced relationship by a suitable retainer 98.

As seen in FIG. 5, a drive mechanism is schematically illustrated for reversing the rotation of the drive roll 12. Specifically, a reverse rotation roll 100 is fixed upon a continuously rotating shaft 102. An intermediate roll 104 is rotatably mounted on a stub shaft 106 and is held in continuous surface engagement with the reverse rotation roll 100 by a connecting a-rm 108 having one end fixed to the stub shaft 106 and its other end rockably supported on the shaft 102. A connecting link 110 extends between an extension 111 on the arm 108 and an ear 112 extending radially outwardly from the ring 74. Thus, as the actuating rod 86 is raised to its extreme position, the ring 74 is rotated through the ear 84 in the counterclockwise direction (FIG. 5). As the ear 112 is thereby moved rightwardly (FIG. 5), it draws the link 110 therewith suchthat the intermediate roll 104 moves into surface engagement with the drive roll 12 and the drive roll 12 is rotated in the reverse direction from its normal rotation.

It will be recalled that during the normal winding operation, the cylinder 78 is completely withdrawn from the armature 46. During this period, the force of magnetic attraction draws the armature 46 firmly against the magnet 42 as well as against the annular member 56 so that the drive roll 12 is operatively connected to the drive shaft 14, substantially as seen in the embodiment of FIG. 3. Then, to brake the drive roll 12, the cylinder 78 is operated to physically separate the armature 46 from the magnet 42 while maintaining engagement between the armature 46 and the annular member 56, substantially as seen in the embodiment of FIG. 4. Since the cylinder 78 engaging the armature 46 is non-rotatable, the drive roll 12 is slowed down and eventually brought to a stop.

However, the further operation of the embodiment of FIGS. 5 and 6 differs from that of the earlier disclosed mechanism. When the drive roll 12 has been brought to a stop and the cylinder 78 is thereupon operated to move the armature 46 to the extreme position shown in FIG. 6 disengaged from both the magnet 42 and the annular member 56, the intermediate roll 104 is moved into engagement with the drive roll 12, as seen in phantom in FIG. 5. The intermediate roll 10'4 remains engaged with the drive roll 12 for a predetermined period during the end finding operation and is thereafter withdrawn opposite to the manner of engagement just described. When the end finding operation has been completed, the cylinder 78 is moved leftwa-rdly, viewing FIG. 6, to a position disengaged from the armature 46. Under the force of magnetic attraction, the armature 46 is again drawn into engagement with the magnet 42 and with the annular member 56 whereby the drive roll 12 is once -more operatively connected to the drive shaft 14 for resumption of the Winding operation.

The invention herein is capable of numerous forms and various applications without departing from the essential features herein disclosed. It is therefore intended and desired that the embodiments herein be deemed illustrative and not restrictive, reference being had to the follow ing claims and not to the specific description herein to indicate the scope of the invention.

What is claimed is:

1. A drive mechanism comprising a base, first and second pre-loaded co-axial bearings rotatably mounted relative to said base and each having concentric races and rolling elements disposed between said races, and regulating means for regulating the operation of a first of said races responsive to operation of a second of said races, control means for selectively regulating the operation of said second race and in cooperation with said regulating means, regulating said operation of said first race, and drive means rotatable relative to said base and operatively connected with a third and fourth of said races for rotating at least said third and fourth races responsive to rotation of the drive means.

2. The mechanism set forth in claim 1 including a load supported on said first race, said control means being operable for selectively connecting said drive means with said first race to regulate operation of said load.

3. The mechanism set forth in claim 1 wherein said regulating means includes a rolling element retainer common to the rolling elements of said first and second bearings.

4. The mechanism set forth in claim 3 wherein said control means includes a coupling member movable between first and second positions and in said first position coupling said drive means and said first race for rotating said first race at a first speed, and in said second position coupling said second race and said base for rotating said first race at a second speed different from said first speed.

5. The mechanism set forth in claim 4 wherein said coupling member is movable to an intermediate position between said first and second positions, said coupling member in said intermediate position coupling said base and said first race for braking said first race.

6. The mechanism set forth in claim 5 wherein said coupling member is an armature, said control means includes a magnet mounted for rotation with said drive means and magnetically coupling said drive means and said armature in said first position, a connecting element, means connecting said connecting element with first race for rotation therewith and for movement axially of said bearings, and resilient means normally biasing said connecting element toward said armature.

7. The mechanism set forth in claim 6 wherein in said intermediate position said base is in abutting engagement with said armature to retard rotation of the armature.

8. The mechanism set forth in claim 6 wherein said drive means includes a drive shaft rotatably mounted relative to said base and said magnet is substantially stationary relative to said drive shaft, and in said first position said armature couples said magnet and said connecting element for rotating said first race with said shaft and in said second position said armature is remote from said magnet and engages said second race for rotating said first race at said second speed.

9. The mechanism set forth in claim 8 wherein a generally cylindrical drive roll adapted to engage a takeup package is mounted on said first race for rotation therewith, and means including a helical groove in the outer periperal surface of said drive roll to guide a strand of yarn onto said package upon rotation of said drive roll.

10. The mechanism set forth in claim 4 wherein said coupling member is an armature, said control means includes a magnet mounted for rotation with said drive means and magnetically coupling said drive means and said armature in said first position, a connecting element, means connecting said connecting element with said first race for rotation therewith and for movement axially of said bearings, and resilient means normally biasing said connecting element toward said armature, an intermediate position of said armature between said first and second positions, said armature in said intermediate position being spaced from said magnet and engaged with said connecting element for braking said first race, and actuating means operable to move said armature between said positions.

11. A drive mechanism comprising a base, a drive shaft rotatable relative to said base, first and second preloaded bearings having inner races mounted on said drive shaft for rotation therewith, said bearings further having outer races and rolling elements disposed between their respective outer and inner races, a rolling element retainer common to the rolling elements of said first and second bearings, a drive roll drivingly supported on the outer race of said first bearing, a magnet fixed to said drive shaft, a ferromagnetic armature movable between first and second positions and in said first position connecting said magnet with said drive roll for rotating said drive roll at a first speed, and in said second position coupling said base with the outer race of said second bearing for rotating said drive roll at a second speed different from said first speed, and actuating means for moving said armature between said first and second positions.

12. The mechanism set forth in claim 11 including a connecting element, means connecting said connecting element with said roll for rotation therewith and for movement axially of said roll and including resilient means biasing said connecting element toward said armature, said actuating means being non-rotatably connected with said base and operable to engage and move said armature to an intermediate position between said first and second positions with said armature remote from said magnet and engaging said connecting element for braking said roll.

13. The mechanism set forth in claim 12 wherein said means mounting said connecting element includes adjustable means for varying the biasing force of said resilient means.

14. The mechanism set forth in claim 11 wherein said drive roll is adapted for surface engagement with a take-up package to rotate the package, and said drive roll having a continuous helical groove in the outer peripheral surface thereof to guide a strand of yarn onto said package upon rotation of said drive roll.

15. A drive mechanism comprising a drive shaft, a. magnet fixed to said drive shaft, a body rotatably mounted on said drive shaft, an armature movable axially of said drive shaft through the field of said magnet, a connecting element, means connecting said connecting element with said body for movement axially of said body into engagement with said armature and for rotation with said body and including resilient means normally biasing said connecting element toward said armature, means mounting said armature for movement from a first position proximate to said magnet and engaging said connecting element to a second position distant from said magnet and disengaged from said connecting element, and actuating means for moving said armature between said positions.

16. The mechanism set forth in claim 15 including a base, said drive shaft being rotatable relative to said base, an intermediate position of said armature between said first and second positions, said armature in said intermediate position being distant from said magnet and operatively connecting said base and said connecting element for braking said body, said actuating means being operable to move said armature to said intermediate position.

17. The mechanism set forth in claim 15 wherein said means connecting said connecting element includes adjustable means for varying the biasing force of said resilient means.

18. The drive mechanism set forth in claim 17 wherein said adjustable means is a screw having a head, and a shank extending through said connecting element and threadedly engaged with said body, and wherein said resilient means is a compression spring coiled about said shank between said head and said connecting element, said screw being adjustable to vary the biasing force of said spring.

19. The mechanism set forth in claim 15 wherein said body is a drive roll having a generally cylindrical surface for engagement with a take-up package to rotate the package, and said roll having a continuous helical groove opening through said cylindrical surface to guide a strand onto the package upon rotation of said drive roll.

References Cited UNITED STATES PATENTS 2,795,146 6/1957 Alfredeen 74-205 2,848,085 8/1958 Mannaioni 192-18 XR 2,950,795 8/1960 Fischer 192-18 XR 2,962,142 11/1960 Straub 192-18 XR 3,011,364 12/1961 Mims 74-798 3,053,101 9/1962 Roberts 74-205 3,227,005 1/1966 Johnson 74-798 3,312,319 4/1967 Carroll et al 192-18 FRED C. MATTERN, J R., Primary Examiner.

J. A. WONG, Assistant Examiner.

US. Cl. X.R. 

